Imprint machine



Dec. 9, 1952 C. L. DOWN EY IMPRINT MACHINE Filed May 29, 1948 3 Sheets-Sheet l .99 1 I /00 J- INVENTOR.

/5 CLEMENT ZEE DOWNEY BY 6 I W W v v Affys.

C. L. DOWN EY Dec. 9, 1952 IMPRINT MACHINE 3 Sheets-Sheet 2 Filed May 29. 1948 INVENTOR. Cum/v1 LEE Dow/v5) JBY Patented Dec. 9, 1952 IMPRINT IWACHIN E Clement Lee Downey, Hannibal, Ma, assignor to Johnson Fare Box Company, Chicago, 111., a

corporation of Delaware Application May 29, 1948, Serial No. 30,0297

7 Claims.

This invention relates to an imprinting machine, and more particularly to a machine for imprinting identification marks upon packaged money.

One of the objects of the invention is the provision of a device whereby rouleaux or coincharged packages, may be neatly imprinted with the identifying mark of a bank or the like, at a rapid rate.

Another object is to include, in a machine of this type, means for rendering the device inoperative after a predetermined number of rouleaux or other packages have passed therethrough.

A further object is to provide a machine of the character stated whichmay be adapted for imprinting rouleaux of various diameters and lengths, that is to say, wrapped coins of various denominations in any monetary system, as well as other commodities of various shapes and sizes.

Another object of the invention is to provide an imprinting machine which is simple, reliable, and free from the need of frequent attention or servicing.

Another object is to provide a machine of the character stated, which easily and quickly may be converted to process articles other than packaged coins, as may be desired.

The foregoing and other objects and advantages are attained by the means described herein and illustrated upon the accompanying drawings, in which:

Fig. 1 is a side elevational view of the imprinting machine showing the gauges set for imprint-' ing rouleaux of dimes, parts of the machine being broken away for clarity of disclosure.

Fig. 2 is a cross sectional view taken on line 22 of Fig. 1, part of the gauge plate being broken away.

Fig. 3 is a fragmentary cross sectional View taken on line 3-3 of Fig. 1.

Fig. 4 is a fragmentary cross sectional 'view taken on line 4-4 of Fig. 1.

Fig. 5 is a fragmentary and elevational view taken on line 55 of Fig. 1.

Fig. 6 is an enlarged cross sectional view of a clutch cam lever, which forms part of the invention, taken on line 6 of Fig. 4.

Fig. '7 is a fragmentary perspective view, showing means for adjusting the device for various denominations of coins.

Fig. 8 is a detailed perspective view of a bell crank and gear segment which forms part of the invention.

Cir

Fig. 9 is a front elevational view of the rouleau counter, taken on line 9--9 of Fig. 2.

Fig. 10 is an end elevational view of the rouleau counter, taken on line I0l0 of Fig. 9.

Fig. 11 is an enlarged perspective View of the counter setting shaft and latch.

For a proper understanding of the present invention, it is necessary to appreciate that the machine disclosed herein is adapted to imprint an identifying mark upon packaged money and the like, such as rouleaux. The machine is adjustable to receive rouleaux of varying lengths and imprint a circumferential mark between the ends thereof.

Ordinarily, coin wrappers have denominational marks, such as pennies, nickels, and the like, printed longitudinally of the roll of coins, substantially centrally thereof. The device of the present invention contemplates the use of coin wrappers having their denominational marks near either or both ends of the rouleaux, in order to provide a blank space circumferentially of the roll of coins, at the approximate center portion thereof, for imprinting an identifying mark thereupon. However, the device may be adapted to imprint a mark at any point between the ends of a rouleau or the like.

Referring to Fig. 1, the imprint machine is shown supported upon a base plate 15, which may in turn be supported by means of the upright post it of a suitable pedestal, the upper end of said post being disposed within the hub iii of the base plate and fixed therein by suitable means, such as the pin I9. The base plate I5 may be of any suitable configuration, but that shown in Fig. 2 is preferred because of its compactness and neat appearance.

Fixed to the base plate i5, upon its longitudinal axis, is the upright irregularly shaped turret bracket 26, vertically bored to receive the rotatable turret shaft 21. The turret bracket 28 may be provided with flanges 22 apertured to receive screws 23 threaded into the base plate 15, as a means of fixing the turret bracket to the base plate.

Keyed to the upper end of the turret shaft 2! is the coin turret 24, which may be in two parts: a body 25, and a cap 25, as shown in Fig. 1, said cap being detachably fixed to the body by means of screws 23. Near its lower extremity, the turret shaft 2| may be provided with a fixed collar 29, the lower face of which may abut the upper race of a thrust hearing (it, the collar and thrust bearing being disposed within a counterbore 3| provided for that purpose in the lower part of the turret bracket 2%. The coin turret 2a is also supported by means of a hub 32 depending from the inner face of the turret cap 26 and abutting the upper face 33 of the turret bracket 29, this support being in addition to the anti-friction support indicated at 2'2, and iii.

The coin turret 2 3 is rotated by means of a miter gear 3 5 keyed to the turret shaft 2!, said gear being in mesh with a mating miter gear 35 keyed to a horizontal clutch shaft which takes its bearing at one end in the upstanding turret bracket portion 33 and at its opposite end in the clutch shaft housing 39. It will be noted that the turret bracket cut away, as at 3-6si3, in order to provide clearance for the mating miter gears 3 l35. The clutch shaft housing may comprise an upright substantially fiat plate provided with outwardly extending feet 3?, apertured for mounting upon the base plate l5 by means of screws ill, transversely of the longitudinal axis of the said base plate.

A free-running gear M is mounted upon the clutch shaft 36, between the housing and the turret bracket 38, and is constantly driven by the meshing pinion :32, which in turn is driven by the motor 43 through the worm dd and worm gear 45, as shown in Fig. 1. The motor, as indicated, may be supported from the lower face of the base plate [5, and may be provided with suitable gear reduction means, as indicated by the gear box it.

The turret 24 is provided with a series of vertical rouleau wells 48, equally spaced upon a radius concentric with and adjacent to the periphery of the turret. of sufficient diameter to loosely receive wrapped coins of the larger diameters for imprinting, such as half-dollars of the U. S. monetary sys tem. Rouleaux are held in a vertical position in the wells 48, supported by the gauge plate :39, the intermediate portion of the rouleaux being in substantial alignment with openings hi3 milled or otherwise provided in the outer wall of the turret body 25. An opening 59 is provided for each rouleau well 48. Since rouleaux containing standard amounts of coins vary in length according to the denomination of the coins, provision has been made for adjusting the gauge plate 59 in order to substantially centralize each denomination of rouleau with the turret wall openings 50. The function of the turret wall openings will be disclosed later.

A second upstanding portion of the turret bracket 29, indicated at St in Fig, 7, is provided with opposed vertical parallel slots '52. The substantially circular gauge plate 59 is provided with a pair of depending lugs 53, spaced apart to permit a free sliding fit vertically uponthe turret bracket portion 5i. A plurality of pins 54, Figs. 1, 2, and 7, inwardly projecting from the depending lugs 53, are adapted to engage the turret bracket slots .52 in a sliding fit, thereby to guide the gauge plate in adjusting it to various elevations in accordance with the requirements of the rouleau denomination to be imprinted. Means for manually elevating the gauge plate .49 may be provided in the form of a setting lever 55, integrally or otherwise associated with the lever plate 53 which is removably attached to the outer faces of the gauge H plate lugs 53, as by means of screws 58.

Means for maintaining the gauge plate it in a selectively adjusted position may be provided, such as a stop block 53, shown in Figs. 2 and 7. The stop block may be cylindrical in form, hav- The rouleau wells 48 are ing buttresses 69 of varying elevations projecting therefrom rotatably mounted upon a pin 5'! pressed into a centrally apertured post 6! provided upon the base plate l5 adjacent the turret bracket 20. For ease in rotating the stop block 59, a knurled disc 62 may be fixed to the lower face thereof. Each buttress 5% is of a different elevation, one for each denomination of rouleau to be imprinted. The upper face of the knurled stop-block disc 52 may carry indicia to indicate the various denominations of rouleauX to be acted upon, as shown at 63. The lower face of the disc 52 abuts the upper face of the post 61,

' As shown in Fig. 7, the lower face 6 3 of a gauge plate lug 53 gravitationally abuts a selected stop block buttress 68. As will be understood, the elevation of each buttress 60 is calculated to position the rouleau of the selected denomination whereby the intermediate portion thereof is in substantial alignment with the turret wall openings 56. The drawings show the machine adjusted for imprinting a rouleau of dimes 61. In adjusting the machine, the operator of the device manually elevates the gauge plate, by means of the setting lever 55, to the point where the-gauge block lug 53 clears the stop block, then manually rotates the stop block 59 until a buttress 69 of the desired denomination is disposed beneath the gauge block lug 53, then permits the said lug to come to rest upon the selected buttress. The depending rib 65 upon the gauge plate 69 is merely for reinforcing said gauge plate.

Rouleaux passing through the machine are imprinted by the rotatable printing roll $3, keyed to the upper end of the printing roll shaft 66 vertically mounted in the forwardly extending portion 69 of the substantially vertical rocker arm T9. The rocker arm is pivotally mounted upon the rocker shaft bracket 1!, by means of the rocker shaft 12, horizontally mounted in the rocker shaft bracket, coplanar with, but at substantial right angles to, the clutch shaft 35. Fixed to the hub 73 of the free-running gear ll and rotatable therewith is the small miter gear M, in mesh with a larger miter gear 15, mounted for rotation upon the rocker shaft 12. As shown in Fig. 3, the rear face of the miter gear 15 abuts the forward face of the rocker arm it. The large miter gear 75, driven by the small miter gear 14, drives a second small miter gear iii, keyed or pinned, as at l8, to the lower end of the printing roll shaft 66. The printing roll 63 may comprise a cylinder of suitable material, such as metal, plastic, or wood, having secured about its periphery a rubber or composition mat provided with the type matter to be imprinted upon the rouleaux. The rocker shaft bracket "ii may be mounted upon the base plate l5 by means of screws H.

An arcuate depression at, Figs. 1 and 2, is provided upon the outer turret wall for each rouleau well 48, the radius of said depressions being substantially that of the printing roll 63. Each turret wall opening 58 is substantially in the center of a depression 86, so that as the printing roll 68 is rotated, the printing surface thereon will contact the paper wrapper of the rouleau 6'! in the well 48 through said wall opening. The rocker arm it) may be provided with yielding means for maintaining the printing roll 68 in contact with that part of the rouleau 6? communicating with the printing roller through the opening 59. The yielding means may be in the form" of a tension spring 8|, Fig. 1, havin one end anchored to a post 82 provided upon the turret bracket upright 38, and its opposite end secured to the rocker arm 19, above the pivotal point.

Since the free-running gear M on shaft 36 is constantly rotating as long as the-motor 43 is energized, the printing roll 68 is also in constant rotation through the miter gears I4, I5, and 16. Means for supplying ink to the printing roller 68 may be provided, such as an inking roller 68a, Fig. 1, mounted to contact the printing surface of the roller 68 and transfer ink thereto by frictional rotation therewith. The inking roller may be mounted on a shaft 682;, parallel with rocker shaft 66, the inking roller shaft 6812 taking its bearing in extensions 680 provided on the rocker member 69.

For each rotation of the free-running gear 4|, the turret 24 is rotated one-third of a revolution, through the medium of a novelclutch means clearly illustrated in Fig. 4. Abutting the flat face 83 of the gear 4Iis a clutch carrier plate 84, also mounted for free-running upon the clutch shaft 36. The clutch carrier plate 84 carries a pivoted clutch trip lever 85, the inner-face of which normally abuts the gear face 93, being held in contact therewith by yielding means, such as a leaf spring 86 fixed to the clutch carrier plate 84. As shown inFig. 4, the clutch trip lever 85 extends radially from the carrier plate 84, being pivoted for movement to and from the gear face 83, the .pivot means being indicated by the pin 86. Abutting the clutch carrier plate 84 and keyed to the clutch shaft 36is a four-tooth ratchet 69, actuated by the pawl 99 pivoted to the carrier plate 84, the ratchet key being indicated at 9!. A clutch pin 92, driven into the gear M and slightly extending from the face 83 thereof in a position to contact the clutch trip lever 85, acts to drive the carrier plate 84 and its pawl 90 to rotate the clutch shaft 36 through the keyed-on ratchet 89. The clutch trip lever 85 is disengaged from the clutch pin 92 by means of a clutch cam block 93, having a beveled or inclined face 94, as shown in Fig. 6, said cam block being fixed to the inner face of the clutch shaft housing 39. As revealed in Fig. 4, the inclined face 94 of the clutch cam block is in the path of the outer end of the clutch trip lever 85 as it is moved by means of the constantly rotating gear 4 I. As the clutch trip lever is driven over the inclined cam face 94,

' it is raised out of contact with the clutch pin 92,

and the carrier plate 84 returned to the starting position shown in Fig. 4, by suitable means, such as a'spiral spring 95. This spring maybe secured to the clutch shaft housing 39 by means of a pin 91 fixed to said housing, with the free end of the spring pinned to the clutch carrier plate 84, as at 81. In its return to starting position, the clutch carrier plate is stopped by means of a clutch trip lever stop 96 fixed to the clutch'shaft housing 39, substantially 90 from the clutch cam block 93. In the exemplified form, the cam block 93 and the trip lever stop 96 are of substantially the same shape except for the inclined face 94 on the former. As illustrated upon Figs. 1 and 2, the members 93 and 96 are secured to the clutch shaft housing 39 by means of screws 98.

Thus it will be seen that as the clutch pin 92, carried by the constantly rotating free-running gear 4|, engages'the clutch trip lever 85, this motion is translated to the clutch shaft 36 through the pawl 99 and the keyed-on ratchet 69. Rotation of the shaft 36 ceases when the clutch trip lever passes over'the cam94, the shaft 36 having made one-quarter revolution. The pin 92 continues to travel in its orbit and upon each revolution thereof the clutch shaft 36 is rotated The motion of the shaft 36 is translated to the coin turret 24, through the meshing miter gears 34 and 35. g 1

While any suitable ratio between the freerunning gear M and the coin turret 24 may be used, the ratio in the exemplified device is three to one. The ratio between the meshing miter gears 35 and 34 is three-quarters to one, since the gear 35 has twenty-four teeth and the gear 34 has eighteen teeth. The timing of the intermittent rotation of the coin turret 24 in the instant'case has been set at twelve seconds per revolution, each movement or /3 revolution requiring one second followed by a pause of three seconds. Figs. 1 and 2 show a rouleau 61 in a rouleau well 48 being stamped or imprinted by the constantly rotating printing roll 68, through the turret wall opening 50 during a three-second pause.

As shown in Fig. 2, the coin turret is provided with three rouleau wells 48, one well being in each of the positions marked A, B, and C during the three-second pause. A complete cycle of the imprinting operation is as follows: A rouleau is dropped by manual or mechanical means into the rouleau well at station A. The rouleau is moved to station B Where it is imprinted during the three-second pause by the printing roll 68, and another rouleau is dropped into the well at station A. The first rouleau is then carried to stationC, having been suitably imprinted, and is gravitationally discharged through openings 98 and 99, Fig. 1, provided in the gauge plate 49 and the base plate i5, respectively, into a bag or other receptacle, while the second rouleau is carried to station B for imprinting and a third rouleau dropped into the turret at station A. This procedure is continued until the desired number of rouleaux of one denomination have been imprinted. Means for selectively limiting the machine to a predetermined number of rouleaux passing through the well at station C may be provided, such as the rouleau counter shown in Figs. 9 and 10, later to be described.

A tubular guide or chute may be provided between the gauge plate aperture 98 and the base plate aperture 99, although this is not necessary, since the said apertures are in vertical alignment with the rouleau well 48 at station C. Means for supporting standard canvas coin bags f r receiving imprinted rouleaux may be provided, such as hooks I98 secured to the lower face of the base plate I5.

Means for tripping the printing roll 68 out of proximity with the turret 24 during the time when the turret is in motion have been provided, said means being synchronized with movement of the turret, as clearly depicted in Fig. 3. Upon the hub 73 of the free-running gear 4 I is a cam IOI, concentric with the said gear and extending substantially 90 about its axis. Pivoted to the forward end of the rocker shaft bracket II is the substantially horizontal cam trip arm I02, the pivot means being the pin I93, which takes a bearing transversely of the said rocker shaft bracket, as shown in Figs. 1 and 2. Oppositethe pivot end, the cam trip arm I82, Fig. 3, carries a trip roller I94, rotatably mounted upon an inwardly extending finger I95 of the cam trip arm. The trip roller I04 normally rests freely upon a ledge I96 laterally extending from the lower portion of the rocker arm I9. Substantially midway of the cam trip arm I02 and upstanding therefrom, in the path of the gear hub cam ItI, is the triangular lug I68. The cam ItI is timed to strike the lug ma approximately at the moment when the clutch pin 92 engages the clutch trip lever 85 on the opposite side of the free-running gear 4|, the camming action and the clutch engagement being synchronized to operate for substantially one second of time. Thus it will be seen that as the cam trip arm m2 is depressed by the action of the cam ItI, the trip roller I94 will cause the rocker arm it? to move about its pivot 72, thereby tripping the printing roller 6t laterally out of proximity with the coin turret 24 during that period of time when the turret is being rotated of a revolution. After the cam IIII has passed over the trip arm lug I53, the printing roll is moved to its printing position by means of the spring BI attached to the rocker arm III, as shown in Fig. 1.

During the tripping of the rocker arm 79, the miter gear 16 remains in mesh with the miter gear I5, since the last named gear takes its bearing on the rocker shaft I2 upon which the rocker arm III is pivoted.

Means for arresting the momentum of the turret 24 in its intermittent movement have been provided for stopping the turret with its rouleau wells in alignment with stations A, B, and C. This is especially important regarding station B, since the turret wall opening 59 must line up with the printing roll 88 so that the latter will properly imprint the rouleau E'I in the well 45. It is also important that the coin turret be stopped with a rouleau well 48 in alignment with the gauge plate aperture 98 and base plate aperture 99, in order that the imprinted rouleau in the well at station C may be discharged therethrough.

The momentum arresting means previously referred to is a clutch brake, illustrated clearly in Fig. 5. As shown therein, the clutch brake comprises a disc I99, keyed as at III? to the outer end of the clutch shaft 35. The periphery of the brake disc I99 is provided with a series of arcuate notches II 2, spaced at 90 intervals. As illustrated, the clutch brake disc, disposed against the outer face of the clutch shaft housing 39, is rotatable only when the clutch mechanism shown in Fig. 4. rotates the shaft 3%. A brake arm II 3 is pivoted at one end to the clutch shaft housing 39, and is provided at its opposite end with a freely rotatable roller H4, adapted to yieldingly engage an arcuate notch H2 in the brake disc. As indicated, the brake arm H3 and the base plate I5 may be socketed, as at I I5 and I I6, respectively, to receive a compression spring H3, which constantly urges the brake arm I13 with its roller IE4 toward the periphery of the brake disc Ids. The brake arm pivot is indicated at H9.

It will thus be seen that as the clutch mechanism operates to rotate the shaft 36 for revolution, any momentum which might be generated upon the release of the clutch pin 92 by the clutch trip lever 35, Fig. 4, is effectively arrested by the clutch brake means illustrated in Fig. 5. As the keyed-on brake disc is rotated by the clutch shaft 36, the brake roller II4 disengages the brake disc notch IIZ with which it is engaged, and engages the following notch II2, thereby to arrest any further movement of the shaft 35 with its cooperating gears and coin turret. The brake roller H4 always tracks upon the peripheral edge of the brake disc IIISas the disc is rotated.

Since rouleaux of various denominations are of different diameters, means for yieldingly maintaining the rouleaux in contact with the printing roll 6-8 have been provided, as illustrated in Figs. 1 and 2. The upstanding central portion I2II of the turret bracket 26, near its upper terminus, has been provided with horizontal slideways I2I, Figs. 1 and 2, one on each side of the turret bracket. A substantially U- shaped platen pressure bar I22 is mounted for reciprocation in the slideways I2I. A pair of freely rotatable pressure rollers I23 are mounted in side-by-side relation in the connecting leg of the U-shaped platen pressure bar I22. The pressure rollers I23 normally project into the area of station B, urged in the direction of the printing roll 68 by the spring loaded bell crank I24, pivoted at I25, Fig. 1, to the turret bracket portion I20.

As detailed in Fig. 8, the bell crank I24 is saddle-like in structure, and upon one side is provided with a depending gear segment I26, the function of which will be disclosed later. The substantially vertical arms I28 and I29 of the bell crank which freely embrace the turret bracket portion I28, are each provided with a slot Ito for engaging the free ends of a pin I3I transversely disposed through the legs of the U-shaped platen pressure bar. A compression spring I32 is seated in the bottom of a vertical recess I33 provided in the turret bracket between the bracket portions 5! and I29. A guide pin I34, having a head I35, is embraced by the spring I32, the said head being thereby urged into contact with the lower face of the connecting portion I36 of the bell crank I24. The action of the compression spring I32 is to force the bell crank portion I36 upwardly, causing the vertical arms I28 and I29 to move to the left, as viewed in Fig. l, by reason of the pivotal connection I25. As the bell crank arms I28 and I29 are thus moved to the left, the platen pressure bar I22 is moved to the left, placing the pressure rollers I23 into yielding contact with the rouleau 67, thereby to urge the rouleau into contact with the printing surface of the rotating printing roll 68. The rouleau, being thus backed up by the pressure rollers I23, is caused to rotate by the action of the rotating printing roll 68, while the rouleau circumferentially receives an inked impression from the printing roll.

As shown in Fig. 1, an elongated horizontal slot I38 is provided transversely of the slideways I2I, through which the platen pressure bar pin I3I is guided as the platen pressure bar I22 is reciprocated in the slideways by means of the bell crank I24.

The guide pin head I35 may be provided with a spherical radius, and the lower face of the bell crank portion I35 may be provided with a cooperating seat I4! as a means of precluding sidewise movement of the guide pin I34 as the bell crank I24 is actuated.

At the end of the three-second period during which the rouleau Ii? is being imprinted, the rocker arm It, carrying the rotating printing roller 68, is tripped by the means hereinbefore described. As the printing roller is thus tripped to the left, as viewed in Fig. 1, the rocker arm Ill carries with it the rack connecting bar I39, indicated in Figs. 1, 2, and 3. The upper surface of one end of the connecting bar is provided with rack teeth I49, which are in mesh with the teeth of the depending bell crank gear segment I26, as shown in Fig. 1. The rack connecting bar is supported for horizontal reciprocation by suitable means, such as the screws I42 and I43, the former threaded into the rear face of the turret bracket 26, the latter threaded into the rear face of the rocker arm I6. Elongated slots I44 and I45 have been provided adjacent each end of the rack connecting bar I39 for the insertion therethrough of the supporting screws I42 and I43 respectively.

As the rack connecting bar I39 is thus carried to the left by the rocker arm I6, the rack teeth I49, in mesh with the bell crank gear segment I26, act to move the bell crank arms I28 and I29 to the right, carrying the platen pressure bar I 22 to the right to release the rouleau 6! from contact with the pressure rollers I23. The tripping of .the printing roller 68 and the releasing of the rouleau from the pressure of the platen pressure barv I22 are, of course, synchronized with the movement of the coin turret 24 as /e of the cycle is completed. Thus, while a rouleauis being carried from station A to station B, the rocker arm 19 is in tripped position andthe platen pressure bar I22 is in retracted position. When the coin turret comes to rest, the printing roller 68 is returned to its operative position by the tension spring. 8I, while the pressure rollers I23 are advanced to contact and support the rouleau against the force of the compression spring I32.

Since rouleaux vary in diameter according to denomination, the elongated slots I44 and I45 in the rack connecting bar I39 permit th platen pressure bar to act upon rouleaux of any diameter with substantially equal pressure upon the rouleaux. The elongated slots I44 and I45 therefore act as a compensating agent in equalizing the pressure between the printing roller 66 and the pressure rollers I23 upon the rouleau at station B, regardless of the rouleau diameter.

The two rollers I23, by virtue of their side-byside relation, serve to centralize the rouleau 61 in the rouleau well 48 at station B against the printing roller 68, the rollers I23 contacting the rouleau at opposite sides of the center line which bisects the rouleau at the printing roller contact point. 1 l

The coin turret .24 may be bodily removed from the turret shaft 2I and replaced with a turret of a different type, as for instance a paper or note currency turret. For this purpose, releasing means may be provided, such as the connecting bar release lever I46, shown in Fig. 1. This releaselever, pivoted to the turret bracket 20 near the lower end thereof at I48, is substantially L-shaped, having the vertical arm I49 in abutting contact with an end face of the rack connecting bar I39; A lifting tab I50, extending beyond the perimeter of the base plate I5, may be provided upon the horizontal arm I5I of the release lever. Lifting the tab I59 will cause the rack connecting bar I39 to move to the left, tripping the printing roller 68 and retracting the platen pressure bar I22. After removal of the turret lock nut I52, the turret 24 may then be removed bodily from th shaftg2l and another type of turret placed thereon.

; Means for selectively limiting the imprinted packages to a predetermined number may be provided, as hereinbefore related. Figs. 2, 9, and delineate a package counter forming a part of the present invention. The counter comprises an upright assembly plate I53 with its component parts, including a cut-off switch I54,

mounted thereon. The assembly plate I53 is provided with an outwardly extending foot member I56 to form a base for anchoring the said assembly plate I53 to the base plate I5 by means of screws I55. The assembly plate is mounted in angular relation to the longitudinal axis of the base plate I5, the inner face being substantially coplanar with the periphery of the coin turret 24, and tangent to the rouleau well at station C.

Slidably mounted for horizontal reciprocation upon the top face of the counter assembly plate I53 is the counting pawl slide I56, provided with a laterally extending counting finger I58 which extends into the area of station C, Fig. 2, between the lower face of the turret 24 and the upper face of the base plate I5. The counting pawl slide I56, as shown in Fig. 10, may be U- shaped in cross section, inverted upon a track I59 provided by rabbeting the upper edge of the assembly plate I53. The counting pawl slide is held against displacement by means of guide pins I60 and NH which traverse said slide, the pins engaging the elongated slots I62 provided in the track I59. The guide pin I69 also serves as a pivot for the counting pawl I63, which actuates the ten-tooth ratchet I64 fixed to a Geneva gear I65 mounted at I66 for rotation upon the outer face of the plate I53.

A forty-tooth gear I68 is rotatably mounted at I69, the teeth of which are adapted to be engaged at intervals by the single tooth I10 of the Geneva gear I65.

Referring to Fig. 2, it will be seen that the counting finger I58, which extends into the area of station C, is in th path of the rouleau 6'! when it is carried by the turret from station E to station C. Therefore, as the rouleau is thus moved to station C, the counting pawl slide I56 by reason of the finger I58, is caused to be moved to the right, while the pawl I 63 actuates the ratchet I64 and its associated Geneva gear I65, the ratchet being thereby advanced tooth by tooth in a clockwise direction of rotation. Means for returning the counting finger I58 to operating position after each movement to the right have been provided, in the following manner.

A three-fingered cam I 98, Fig. 2, is fixed to the turret shaft 2| for rotation therewith, said rotation being intermittent, as previously recited. The position of the cam I98 on the turret shaft is substantially coplanar with the counting finger I 58, shown in Figs. 9 and 10. As indicated on Fig. 1, the three-fingered cam is provided with a collar I99, through which means may be applied for fixing the cam to the turret shaft, such as the setscrew 209.

Coplanar with the cam I98 is the substantially horizontal counting finger retrieving arm 29I, pivotally mounted at 202 to the lower face of the turret bracket extension which carries the platen pressure bar I22. As shown in Fig. 2, the retrieving arm 29I extends in irregular form from the pivotal point 292 to the counting finger I58, the said arm being provided at its free end with a projection 263 which bears against a side of the counting finger I 58. Fig. 2 shows the counting finger in position to be acted upon by a rouleau 61, having been brought to this position by reason of a cam point 264 bearing against the side of the retrieving arm at 295 as the cam is rotated by the turret shaft 2I. Actually, this position of the counting finger I58, retrieving arm 29I, and cam I98, as shown in Fig. 2, is attained immediately upon the initial movement of the coin turret 24, so that by the time the rouleau at station E reaches station C, the counting finger is in the path of the rouleau, to move the said finger to the right and actuate the Geneva gear I65 through the counting pawl and ratchet HES-KM. As the counting finger I53 is moved to the right, the retrieving arm Edi is moved back about its pivot 2&2, a clearance being provided upon the retrieving arm at 2% to preclude interference with the cam point Since the counting finger I58 ofiers no resistance within the limits of station C, the rouleau is free to fall through the discharge ports 9%99. The counting finger I58 remains in the inoperative position during the three-second pause, and again assumes the position in Fig. 2 immediately upon the beginning of the one-third revolution of the coin turret being carried there by the retrieving arm projection 2% by reason of the action of the cam ids upon the retrieving arm.

The ratio between the Geneva gear Ibfi and the forty-tooth gear I68 being two to one, the Geneva gear tooth Ill will move the gear IE8 a distance of two teeth, or one-twentieth of a revolution, upon each rotation of the Geneva gear.

Upon the assembly plate I53, below the gear IE8, is mounted a pillow block I? I, through which is slidably and rotatably mounted the counter setting shaft I'I2, said shaft extending beyond each end of the pillow block. Fixed near the inner end of the setting shaft IE2 is the cutoif rod housing H3 including a longitudinally apertured vertically extending arm lid. The cut-off rod H5 is slidably mounted for vertical reciprocation in the arm I'M, being provided with suitable means for precluding rotation, such as the pin Elli extending through the cut-off shaft and into the vertical slots I'iB provided in the upper face of the vertical arm I'M. Near the upper end of the cut-off rod I75 and laterally extending therefrom is the cut-off bar I79 which operates to cut off the electric switch I55 and stop the machine when a predetermined number of rouleaux have been acted upon, as will be explained later in detail. The cut-off bar H9 may be fixed to the cut-off rod by means of screws Ill.

The cut-off rod I75 is normally urged upward by suitable means, such as the compression spring I86 in encircling relation with the cutoff rod, said springabutting the lower face of the cut-off bar are and the upper face of the vertical arm ild. Upward movement of the cutoff rod may be limited by means of a stop pin ISI inserted transversely through the cut-off rod near its lower terminus, said pin abutting the lower face of the vertical arm I'M, as shown in Figs. 9 and 10, when the cut-off rod H5 is in normal extended position. 7

The outer face of the gear I63 is provided with a series of abutments or slightly extending pins E32, Hi3, and ISA, arranged in spaced circles concentric with the axis of said gear, each circle having a different number of abutments or pins. An inwardly extending pin E is provided on the cut-on"- rod H5, near its upper terminus. The inner face of the pin I85 is normally maintained in abutment with the outer face of the fortytooth gear H 8, Fig. 10, by suitable means, such as the spring I36, Fig. 9, fixed to the inner end of the setting shaft I72 and acting upon the vertical arm lid. The setting shaft, near its outer end, may be provided with a series of notches I88, iBG, Hi9; ISI, the last named notch being for the purpose of setting the counting mechanism in neutral or non-operative position, this position being shown in Figs. 2, 9, 1i) and 11. The notches I88, I89, and I98 are spaced apart in correspondency with the concentric circles of pins I82, I83, and I8 5.

The setting lever I'l2 may be maintained. in proper adjusted position by any suitable means, such as the setting latch m2, shown in perspective in Fig. 11. The setting latch is pivoted to the outer edge, of the counter plate I53, as at I93, for free pivotal movement thereon, and may be provided with an extension I95 for the purpose of increasing the gravity of the latch as it rests in a selected setting shaft notch.

As hereinbefore related, the number of pins in each concentric circle differs. In the exemplifled form, pins I82 in the outer circle are ten in number, equally spaced, or one pin for every four teeth on the gear I88. The pins I33 in the adjacent circle are four in number, equally spaced, or one pin for every ten teeth in the gear I68, while the smallest circle contains only two pins, diametrically opposed, one for each twenty teeth. No pins are provided in the neutral portion of the gear I68.

The package counter may be set to open the electric switch I54 to stop the machine when any predetermined number of rouleaux have been acted upon, these numbers in the exemplified case being twenty, fifty, and one hundred.

Assuming that the operator wishes to have the machine imprint twenty rouleaux of one denomination, he first sets the gauge plate so to the proper elevation for the selected denomination by means of the stop block 59 in the manner hereinbefore recited. He then manually turns the setting shaft I72 counter-clockwise, as viewed in Fig. 10, by means of the setting lever I 95, against the force of the spring I89, until the latch I92 becomes disengaged from the setting shaft notch with which it is engaged, and pushes the setting shaft in until the latch IE2 is in line with the notch I88. The setting lever is then released and the latch I92 permitted to gravitationally engage the notch I88. The face of the cut-off rod pin I will now be in abutment with the outer face of the fortytooth gear, in the direct path of the pins I82, being maintained in this position by spring I89.

The motor as may then be energized-by moving the switch arm I to the substantially horizontal position shown in Fig. 9, to be acted upon by the cut-off bar H9. which it contacts. If the machine has previously been used for imprinting rouleaux of fifty or one hundred lots, it maybe necessary to set the counter manually in order to place the cut-oh: rod pin I 85 in proper relation with one of the pins I82 for stopping the machine at the end of twenty imprints. 'This may be done by manually'reciprocating the counter pawl slide 55 by means of the counting finger I58, until one of the pins Hi2 contacts and depresses the cut-off rod pin I85 to the point where the switch arm ii -5' is depressed by the cut-off bar I19 to cut off the electric power'and stop the machine. At this point the counting mechanism is set to be automatically rendered inoperative at the compl tion of every twenty rouleaux imprintings.

The operator then resets the switch and begins feeding rouleaux to the turret at station A. The rouleaux are moved in succession to the imprint station E and the discharge station C, where each rouleau moves the counting finger I58 to the right, as. viewed in Figs. 2 and 10; This move ment is translated to the Geneva gear I65 through the pawl and ratchet I63I64, to move the Geneva gear one-tenth of a revolution. When twenty rouleaux have passed through the discharge station C, the Geneva gear I65 has been rotated two complete revolutions, and the single tooth I'm thereon has moved the forty-tooth gear I68 for a distance of four teeth, which equals the distance between the pins I82. At this point a pin I82 will contact and depress the cut-off rod pin I 85, moving the associated cut-on" bar I79 downward to actuate the switch I54, thereby rendering the machine inoperative until the switch is again reset. If the rouleaux are discharged into a bag, as is common practice, the bag is removed from the hooks It!) and replaced with an empty one and the operation repeated. The machine now needs no resetting if rouleaux are to be imprinted in lots of twenty, since the pins I32 are in proper relation with the cut-01f rod pin I85 .for twenty-lot rouleaux of any selected denomination.

If rouleaux are to be imprinted in lots of fifty or one hundred, it may be necessary to reset the counting mechanism as hereinbefore related, in order to bring the cooperating pins in proper relation with each other before initiating operation on the first lot. It will be understood that the setting latch I92 should engage the setting shaft notch I89 for imprinting-rouleaux in lots of fifty, and that the said latch will engage not-ch I88 for lots of one hundred. If an unlimited number of rouleaux are to be imprinted, the

counting mechanism may be disposed in the neutral position shown in Fig; 9, with the latch I92 engaging the notch IQI.

When the counter is set for lots of fifty rouleaux the Geneva gear IE5 rotates five revolutions to move the gear I63 a distance of ten teeth before the electric switch I56- is actuated to stop the machine. By the same token, the Geneva gear rotates ten revolutions to move the gear I68 a distance of twenty teeth, or a half revolution, for breaking the electric circuit when the counter is set for lots of one hundred rouleaux.

It should be noted that the package counter is actuated only when a rouleau is carried to and discharged from station C. Regardless of the number of revolutions of the turret 24, therefore, only those rouleaux discharged at station C will be counted.

It will be understood, of course, that the gear ratios, timing, and package counter settings need not be those herein specified, since other ratios, timing and settings are possible within the spirit of the invention.

In conclusion it is to be understood that the device herein disclosed is but one of a number of possible arrangements or combinations of constituent parts that may be utilized in reducing the invention to a useful or practical form. Many of the machine parts are capable of considerable modification, and the substitution of various equivalents within the bounds of accepted engineering practice of machine design may be made within the scope of the appended claims, without departing from the spirit of the invention.

The machine may be provided with a suitable housing, not shown, for protecting the gears and other mechanism against the entry of dust and other extraneous matter, and for reducing physical hazards incident to the use of the machine. Such a housing, of course, would be provided with suitable openings for gaining access to the turret and to the various operating levers during operation of the device.

What is claimed is:

1. A machine for marking an elongated rouleau which comprises a horizontal gauge plate, a printing wheel rotatably mounted above Said gauge plate on a substantially vertical axis, means for advancing'a rouleau along the gauge plate with the longitudinal axis of the rouleau disposed vertically, the lower end of the rouleau resting on the gauge plate, to a printing station adjacent the printing wheel, a back-up member spaced from the printing wheel and engaging the rouleau when at the printing station to hold the rouleau against the printing wheel, means for rotating the printing wheel, and means for bringing the printing wheel into engagement with the rouleau as the printing wheel turns to print indicia on the side of the rouleau.

2. A machine for marking elongated rouleaus which comprises a turret rotatable upon a vertical shaft, said turret having at least one upright open-ended rouleau-receiving socket adjacent the periphery thereof, a horizontal gauge plate disposed below the turret for'suppo'rting in upright position thereon a rouleau, the location of the plate being such that at least the upper portion of the rouleau is in said socket, drive means for turning said turret to shift the socket successively toa station in which a rouleau is deposited in said socket, a printing station and a discharge station, saiddrive means arrestingrotation of the turret for a predetermined length of time when the socket thereof arrives at each of said stations, a printing wheel rotatably mounted at the printing station on a shaft substantially parallel to the shaft of the turret and outside the turret, said printing wheel engaging one side of the rouleau while the turret is arrested with the socket at the printing station, a pair of rotatably mounted back-up rolls inside the turret to engage the opposite side of the rouleau and hold the rouleau against the printing wheel, means for turning the printing wheel to cause the rouleau to turn between the printing wheel and the back-up rolls and means operating in timed relation with the drive means for withdrawing the printing roll and the back-up rolls from the periphery of the turret while the turret turns.

3. A machine for marking an elongated rouleau which comprises a turret rotatable upon a vertical shaft, said turret having a plurality of angularly spaced upright open-ended rouleau receiving sockets adjacent the periphery thereof, a horizontal gauge plate below the turret for supporting upright rouleaus in said sockets, the location of the plate being such that at least the upper portion of each rouleau is in one of the sockets, drive means for turning said turret toshift the sockets successively to a station in which rouleaus are deposited in said sockets to a printing station and a discharge station, said drive means arresting rotation of the turret for a predetermined length of time when one of the sockets arrives at each station, a printing wheel at the printing station mounted on an elongated shaft, said shaft being outside the turret and being substantially parallel to the shaft of the turret, said printing wheel engaging one side of the rouleau in the socket at the printing station, a pair of rotatably mounted back-up rolls inside the turret to engage the opposite side of the rouleau to hold the rouleau against the printing wheel, a driven bevel gear mounted on said shaft remote from the printing wheel, a main bevel gear in mesh with 15 the driven gear, the axis of the main bevel gear extending transversely of the shaft of the turret, means pivotally supporting the printing wheel shaft on the axis of the main bevel gear, means for holding the printing wheel and back-up rolls in engagement with'the rouleau when the turret .is at rest with one of the sockets at the printing station, means for turning the main bevel gear to drive the printing wheel and turn the rouleau between the printing wheel and the back-up rolls, and means operating in timed relation with the turret turning means for withdrawing the backup rolls from the periphery of the turret and for swinging the printing wheel shaft around the axis of the main bevel gear and away from the periphery of the turret when the turret turns.

4. A machine in accordance with claim 3 characterized by the fact that the back-up rolls are mounted on a horizontally sliding carriage inside the turret, that the carriage is linked to the shaft of the printing wheel so that the rolls are withdrawn from the periphery of the turret when the printing wheel shaft is swung away therefrom, that means resiliently urge the carriage in a direction to bring the back-up rolls toward the periphery of the turret, and that the linkage contains a lost motion connection, whereby the backup rolls and the printing wheel are both resiliently urged against the rouleau when the turret is at rest with one of the sockets at the printing station.

5. A machine in accordance with claim 3 characterized by the fact that the back-up rolls are mounted on a horizontally sliding carriage inside the turret, that the carriage is linked to the shaft of the printing wheel so that the rolls are withdrawn from the periphery of the turret when the printing wheel shaft is swung away therefrom, that means resiliently urge the carriage in a direction to bring the back-up rolls toward the periphery of the turret, that the turret includes a downwardly extending peripheral skirt, and that the linkage contains a lost motion connection, whereby the back-up rolls and the printing wheel are both resiliently urged against the rouleau when the turret is at rest with one of the sockets at the printing station, the back-up rolls holding the rouleau against the skirt of the turret.

6. A machine in accordance with claim 3 characterized by the fact that the gauge plate is slidably mounted for vertical sliding toward and away from the turret and that means is provided for holding the gauge plate at predetermined elevations, whereby the printing wheel prints indicia on the rouleau at a predetermined height.

7. A machine in accordance with claim 3 characterized by the fact that the means for turning the main bevel gear is a driving bevel gear mounted on an axis substantially perpendicular to the axis of the printing wheel shaft and that a cam is attached to said driving bevel gear to turn with it, said cam engaging the support of the printing wheel shaft to swing the printing wheel shaft on the axis of the main bevel gear and away from the periphery of the turret when the turret turns CLEMENT LEE DOWNEY.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,130,682 Augensen Mar. 2, 1915 1,267,167 Baker May 21, 1918 1,892,545 Ward Dec. 27, 1932 2,137,013 Bradley Nov. 15, 1938 2,341,409 McDonell Feb. 8, 1944 2,399,630 Friden May 7, 1946 2,415,854 Shefiield Feb. 18, 1947 2,500,871 Robbins Mar. 14, 1950 

